CN116044773B - High-temperature magnetic drive pump and design and development method thereof - Google Patents
High-temperature magnetic drive pump and design and development method thereof Download PDFInfo
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- CN116044773B CN116044773B CN202211649199.1A CN202211649199A CN116044773B CN 116044773 B CN116044773 B CN 116044773B CN 202211649199 A CN202211649199 A CN 202211649199A CN 116044773 B CN116044773 B CN 116044773B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
- F04D29/0462—Bearing cartridges
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
Abstract
The application relates to a high-temperature magnetic drive pump and a design and development method thereof, wherein the scheme comprises the following steps: uniformly arranging a plurality of spiral gaps with the same shape and length on the surface of an inner hole of a bearing seat of a magnetic drive pump along the circumferential direction, arranging openings of the spiral gaps on the surface of the inner hole, and arranging the tail end of the spiral gaps in a base body of the bearing seat; calculating the expansion difference between the room temperature and the design temperature required by the magnetic drive pump at the matching surface between the bearing seat and the sliding bearing; determining the size of an inner hole of the bearing seat according to the expansion difference and the outer diameter size of the sliding bearing and the interference requirement at the design temperature; checking the strength of the supporting sheet of the bearing seat and continuously adjusting the structural size and shape of the supporting sheet until the stress of the supporting sheet is less than or equal to the allowable stress of the bearing shaft material. The device is suitable for the requirement of no leakage of the conveying medium under the conditions of high temperature and variable temperature, and has the advantages of low operation vibration, high efficiency, high reliability and convenient installation and maintenance.
Description
Technical Field
The application relates to the technical field of magnetic pumps, in particular to a high-temperature magnetic transmission pump and a design and development method thereof.
Background
As shown in fig. 1 and 2, the present magnetic drive pump is composed of a pump body, an impeller, a pump cover, an outer magnetic rotor and a drive part, an inner magnetic rotor, a thrust ring, a spacer sleeve, a pump shaft, a shaft sleeve, a sliding bearing assembly, a motor and the like, wherein the sliding bearing is installed in an inner hole of the pump cover through a sliding bearing seat. The inner magnetic rotor and the outer magnetic rotor are separated by a nonmagnetic isolating sleeve, and the isolating sleeve is fastened with the pump cover by a sealing gasket. The inner magnetic rotor connected with the impeller is driven by the outer magnetic rotor connected with the motor through the action of a magnetic field, so that the pump realizes the medium conveying in a fully-sealed and leakage-free manner. Because of the leak-free characteristic, the magnetic pump is widely applied to the fields of petrochemical industry and the like for conveying flammable and explosive, highly toxic, noble and corrosive media.
Because the inner rotor component of the magnetic pump is immersed in the medium, as a support for the inner rotor component, a sliding bearing is generally adopted for the bearing, and the bearing is lubricated by self-conveying medium. For the occasion that needs long-period reliable operation, in order to improve the operation reliability of the magnetic pump, the sliding bearing needs to be made of wear-resistant ceramic materials, such as silicon carbide ceramics widely used in the magnetic pump at present. As is well known, silicon carbide ceramics have a very low coefficient of thermal expansion, about 4X 10-6/DEG C, while the metallic material used as a bearing seat has a relatively high coefficient of expansion, typically martensitic stainless steel is 11X 10-6/DEG C, while austenitic stainless steel has a coefficient of expansion of about 2.5-4 times that of a silicon carbide bearing at 16X 10-6/DEG C. This will cause a large expansion difference between the silicon carbide sliding bearing and the metal bearing housing base. Taking the working temperature of 320 ℃ of a conventional heat conduction oil pump as an example, when the outer diameter of the sliding bearing is 100mm, the expansion difference between the sliding bearing made of silicon carbide and the metal bearing seat when the temperature rises to 300 ℃ is at least 0.21mm.
This results in the following: (1) If clearance or transition fit is adopted for convenient assembly and maintenance, when the sliding bearing runs under a high-temperature working condition, the clearance between the sliding bearing and the bearing seat is larger due to expansion difference, and the clearance is quite large, so that the sliding bearing with the size as described above has a fit clearance of about 0.2mm, and the sliding bearing is seriously loosened, so that the vibration of a pump is increased, and the fragile silicon carbide ceramic sliding bearing is easy to damage; meanwhile, the gap is increased, so that the sliding bearing deviates from the axis of the bearing seat base body, the rotor deviates from the axis of the base body under the action of gravity or internal hydraulic radial force, scraping abrasion is generated at the gap part of the sealing ring with a small gap, the service life is shortened, meanwhile, the rotor vibration is increased due to friction, the use reliability of the fragile sliding bearing is adversely affected, and the silicon carbide ceramic sliding bearing is easy to crack and damage. Therefore, the application on high temperature magnetic pumps does not basically use a clearance fit, but rather an interference fit as described below.
(2) The interference fit can prevent loosening at high temperature. Because of the large expansion difference, the interference needed to avoid the loose of the sliding bearing and the bearing seat is large, and for example, the matching size of the sliding bearing with the diameter of 100mm is needed to be at least 0.21mm. Because the elastic modulus of silicon carbide reaches about 450GPa, the bending resistance and the shear strength are lower than those of metal, and the silicon carbide belongs to brittle materials. Therefore, after assembly, the stress at the sliding bearing is very high in a normal-temperature cold state, and the stress at the guide groove is already higher than the compressive strength of the silicon carbide material, so that the sliding bearing is easy to crack and damage. Even if the magnetic pump is not damaged at first, cracking damage can occur under the influence of vibration during the cold start of the magnetic pump. The large interference causes inconvenient on-site assembly and disassembly, and a high-temperature heater is required to be arranged, which is disadvantageous to the continuous safe and reliable operation of the device for guaranteeing the petrochemical process.
(3) However, the stress caused by interference fit is very large and can reach about 1000MPa, even the tensile strength of the common metal material is exceeded, and the yield stress of the common metal material of the magnetic pump is far exceeded, so that the bearing seat is deformed and even broken due to yield. The stress acting on the bearing seat also causes larger deformation of the bearing seat, the size of the outer circular surface is obviously increased to 0.12mm, and the bearing seat can be installed in the positioning hole of the pump cover after being subjected to repair processing until the size of the outer circular surface is similar to that of the inner hole of the pump cover; however, when the high-temperature working condition is adopted, the thermal expansion coefficient of the silicon carbide bearing is small, the expansion amount is small, the interference with the bearing seat base body is reduced, the deformation caused by the interference stress borne by the bearing seat base body is reduced, the gap between the bearing seat base body and the inner hole of the freely-expanded pump cover is enlarged, the eccentricity between the sliding bearing part and the pump cover is caused, the eccentricity between the rotor and the base body is caused, the scraping of the impeller sealing ring part on the rotor is caused, the service life is shortened, the vibration is increased, and the sliding bearing is easy to crack. And once the sliding bearing is broken, the rotor of the magnetic pump collides with the isolation sleeve, so that the isolation sleeve is damaged, and a serious safety accident of high-temperature inflammable medium leakage is caused.
Therefore, the existing high-temperature magnetic pump adopts the design that the sliding bearing is in small interference fit with the bearing seat, the fastening screw props against the sliding bearing to prevent rotation, and meanwhile, the clearance of the impeller sealing ring is obviously increased to prevent friction. Although the sealing ring cannot be rubbed, the backflow loss at the sealing ring is obviously increased due to the increase of the clearance of the sealing ring, the efficiency of the magnetic pump is obviously reduced, and the energy consumption is larger; meanwhile, due to the small interference fit design, the gap between the sliding bearing and the bearing seat is increased to be loosened at high temperature, the sliding bearing is easy to generate local cracks to damage after long time under the action of high temperature and vibration force, and the bearing seat is easy to deviate to one side due to the fact that the bearing seat is matched with the pump cover to be loosened, so that the rotor is eccentric, and vibration is increased.
In summary, the current magnetic pump sliding bearing structure design has the problems of high Wen Songdong and the problem that the coaxiality cannot be always maintained. The existing high-temperature magnetic pump has the hidden trouble defect of affecting reliable operation, and the probability of causing accidents can be reduced only by checking the abrasion condition by stopping and disassembling for many times. The maximum risk hidden danger of the magnetic drive pump when being applied to high temperature operating mode at present is slide bearing's reliability, though barely can be used to high temperature operating mode, the vibration is great, and the hidden danger of use is many, and the reliability is relatively poor, examines maintenance interval short, is unfavorable for petrochemical industry to the requirement of equipment long period safe and reliable operation, and the fault rate is higher, and the security risk is great, and operating efficiency is lower and causes the energy consumption great moreover, is unfavorable for energy saving and emission reduction, reduces the target of carbon emission.
Therefore, a novel design for ensuring that the sliding bearing is not loose and the coaxiality can be always maintained is needed, the problem that the existing high-temperature magnetic pump cannot be prevented from being simultaneously maintained in looseness and coaxiality is thoroughly solved, the magnetic pump can reliably and efficiently run for a long period under the working conditions of high temperature and variable temperature, and the magnetic pump is easy and efficient to maintain, disassemble and assemble.
Content of the application
The present application aims to solve the above problems in the prior art, and provides a high-temperature magnetic drive pump and a design and development method thereof.
The core of the application is that the structural rigidity of the surface of the bearing seat supporting part is reduced, the stress generated during excessive assembly is reduced, the damage to the sliding bearing is avoided, the assembly and disassembly force is reduced, the maintenance is convenient, the matching size between the bearing seat and the outer side mounting matrix is not influenced, and the coaxiality between the sliding bearing assembly and the mounting matrix is always kept. The application only carries out optimal design development to the structure of the sliding bearing part of the high-temperature magnetic drive pump, and the rest structures are all in the prior art.
In order to achieve the purpose of the application, the application adopts the following technical scheme: a high-temperature magnetic drive pump comprises the following steps:
s00, uniformly arranging a plurality of spiral gaps with the same shape and length on the surface of an inner hole of a bearing seat of a magnetic drive pump along the circumferential direction, arranging openings of the spiral gaps on the surface of the inner hole, and arranging the tail end of the spiral gaps in a substrate of the bearing seat;
s10, calculating the expansion difference between the room temperature and the design temperature required by the magnetic drive pump at the matching surface between the bearing seat and the sliding bearing;
s20, determining the size of an inner hole of the bearing seat according to the expansion difference and the outer diameter size of the sliding bearing and the interference requirement at the design temperature;
s30, checking the strength of the supporting thin sheet of the bearing seat, and continuously adjusting the structural size and/or shape and/or number of the supporting thin sheet until the stress of the supporting thin sheet is smaller than or equal to the allowable stress of the bearing seat material so as to complete the design of the high-temperature magnetic drive pump;
wherein the supporting sheet is positioned at the matching position of the bearing seat and the sliding bearing.
Further, in step S00, the spiral slit is shaped as an involute or a circular arc or an approximate circular arc.
Further, in the step S00, the ratio of the radial distance between the tail end of the spiral gap and the surface of the inner hole of the bearing seat to the length of the spiral gap is 0.1-0.25.
Further, in step S00, a distance is set from a spiral start of the spiral slit such that the thickness of the support sheet is at least 0.5mm thick, wherein the spiral start intersects the inner surface of the bearing housing bore.
Further, in the step S00, the number of the spiral slits is not less than six.
Further, in step S00, the lengths of the beginning and end portions of adjacent spiral slits are located at the same circumferential azimuth angle in the circumferential direction, so that the inner surface of the bearing seat forms a sheet-shaped structure, one end of the sheet is suspended, and the other end of the sheet is fixed on the base body of the bearing seat to form an cantilever type sheet.
Further, in the step S10, the expansion difference is calculated according to the linear expansion coefficient of the bearing seat, the linear expansion coefficient of the sliding bearing material, the size of the matching part of the outer diameter of the sliding bearing and the design temperature required by the magnetic drive pump.
Further, in the step S20, the inner hole size of the bearing seat is determined according to the expansion difference, the outer diameter size of the sliding bearing and the interference, wherein the interference is to increase the pretightening force on the basis of the expansion difference, so that the expansion difference is increased, and the expansion difference is replaced by the interference, so that the anti-loose effect at high temperature is realized.
Further, the interference is 115% -130% of the expansion difference.
The high-temperature magnetic drive pump is manufactured through the design and development method of the high-temperature magnetic drive pump.
Compared with the prior art, the application has the following beneficial effects:
1. when the bearing seat adopting the method generates the same deformation quantity caused by the interference structure, the force required by bending deformation of the cantilever beam type thin sheet is far smaller than that of the cylindrical rigid thick-wall cylinder body, so that the stress is obviously reduced under the condition of large excessive assembly of the sliding bearing and the bearing seat, the assembly and disassembly are easy, and the bearing seat can normally work under the normal temperature and cold state; when the magnetic pump works at the design temperature, the interference between the bearing seat and the sliding bearing is reduced due to temperature rise, but the bearing seat and the sliding bearing are still in an interference fit state and are tightly matched, so that the magnetic pump is not loosened at high temperature, and meanwhile, the coaxiality between the bearing seat and the sliding bearing is maintained, so that the problem and the defect of the original high-temperature magnetic pump are thoroughly solved;
2. the integrated thin sheet on the inner surface of the bearing seat adopting the method can be formed by adopting a wire cut electrical discharge machining method, is uniformly distributed along the circumference, and cuts out a plurality of gaps with closed ends to form a plurality of thinner supporting sheets with the same size. The gap formed by wire cutting is a movable space required by radial bending deformation of the supporting sheet, so that the structural rigidity of the surface of the supporting part of the bearing seat can be reduced, the stress generated during large excessive assembly is reduced, the damage of the sliding bearing is avoided, the assembly and disassembly force is reduced, the maintenance is convenient, the matching size between the bearing seat and the outer side mounting base body is not influenced, and the coaxiality between the sliding bearing assembly and the mounting base body is always kept;
3. the supporting sheet has undergone large excessive stress by bending deformation, so that the matching part of the bearing seat and the pump cover is basically not influenced by interference fit of the inner hole, and can freely follow expansion and contraction of the pump cover together, always keep coaxiality with the pump cover and achieve the effect of temperature change self-adaption;
4. according to the anti-loosening device, the interference is increased when the size of the inner hole of the bearing seat is determined, the pretightening force generated by the interference of the increased part is used as the anti-loosening requirement at high temperature, and the friction coefficient of the sliding bearing pair is very low, so that only a small pretightening force is required to be increased, and the anti-loosening effect is achieved.
Drawings
FIG. 1 is a schematic diagram of a prior art magnetic pump;
FIG. 2 is an enlarged schematic view of the slide bearing portion of FIG. 1;
FIG. 3 is a flow chart of the design of the present application;
FIG. 4 is a block diagram of a plain bearing component of the present application;
FIG. 5 is a side view of FIG. 4;
FIG. 6 is an enlarged view of a portion of the mating portion of the slide bearing assembly of the present design;
fig. 7 is a partial enlarged view of fig. 6.
In the figure, 1, a bearing seat; 2. a sliding bearing; 3. a slit; 4. a sheet; 5. a spiral line; 31. the starting end of the gap; 32. the slit ends.
Detailed Description
The following description of the embodiments of the present application will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all, of the embodiments of the present application. All other embodiments obtained by a person of ordinary skill in the art based on the embodiments in the present application are within the scope of the protection of the present application.
It will be appreciated by those skilled in the art that in the disclosure of the present application, the terms "longitudinal," "transverse," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," etc. refer to an orientation or positional relationship based on that shown in the drawings, which is merely for convenience of description of the present application and to simplify the description, and do not indicate or imply that the apparatus or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore the above terms should not be construed as limiting the present application.
Example 1
As shown in fig. 3, the design and development method of the high-temperature magnetic drive pump comprises the following steps:
s00, uniformly arranging a plurality of spiral gaps 3 with the same shape and length on the surface of an inner hole of a bearing seat 1 of a magnetic drive pump along the circumferential direction, arranging openings of the spiral gaps 3 on the surface of the inner hole, and arranging the tail ends of the spiral gaps in a matrix of the bearing seat 1;
in the present embodiment, as shown in fig. 4 and 5, the spiral slit 3 is shaped as an involute or is replaced by an approximate circular arc, and its end is located at a radial distance h from the inner hole surface of the bearing housing 1 1 The length ratio X of the spiral slit 3 is 0.1-0.25, the start of the spiral slit 3 is from a certain distance from the start of the spiral line 5, so that the thickness h of the start sheet 4 0 Has a solid wall thickness of at least 0.5 mm.
Preferably, the number of the gaps 3 is not less than 6, the number is between 6 and 16, the angle of each gap 3 along the circumferential direction is larger than (360 °/the number of the gaps 3), namely, as shown in fig. 6 and 7, the length of the spiral gaps 3 is limited, the angle of each gap 3 along the circumferential direction is guaranteed to be larger than (360 °/the number of the gaps 3), namely, the lengths of the initial end and the tail end of the adjacent gaps 3 are located at the same circumferential azimuth angle Λ along the circumferential direction, so that the initial end and the tail end of the adjacent gaps 3 are located at any position on the inner hole surface of the bearing seat 1, at least pass through one gap 3, the initial end and the tail end of the gap 3 pass through two gaps 3, so that the inner surface of the bearing seat 1 becomes a sheet 4-shaped structure, one end of the sheet 4 is suspended, the other end of the sheet 4 is fixed on the bearing seat 1, cantilever type sheet 4 is formed, the solid thickness between the gaps 3 is the wall thickness h of the sheet 4, and the length between the initial end and the tail end of the adjacent gaps 3 is the cantilever beam stress point.
S10, calculating the expansion difference between the room temperature and the design temperature required by the magnetic drive pump at the matching surface between the bearing seat 1 and the sliding bearing 2;
in the present embodiment, the design temperature T is determined according to the design temperature T required by the high-temperature magnetic pump 2 It can be seen that the temperature increases by Δt compared with the normal temperature; the size of the outer diameter matching part of the sliding bearing 2 is known as d, and the linear expansion coefficient alpha of the metal bearing seat 1 1 Linear expansion coefficient alpha with silicon carbide sliding bearing 2 material 2 The expansion difference Δd=d×Δt (α) at the mating surface between the metal bearing housing 1 and the silicon carbide sliding bearing 2 is calculated 1 -α 2 )。
S20, determining the size of an inner hole of the bearing seat 1 according to the expansion difference and the outer diameter size of the sliding bearing 2 and the interference requirement at the design temperature;
in this embodiment, the difference (d- Δd) between the outer diameter of the sliding bearing 2 and the expansion difference is preferably increased by 15% -30% based on the expansion difference Δd (because the friction coefficient of the sliding bearing 2 pair is very low, only a slight pre-tightening force is needed to achieve the anti-rotation effect), which is the designed interference Δd s This is used as the initial bore size (d- Δd) of the bearing housing 1 s ). The pretightening force generated by the interference of the part is increased and is used as the requirement of looseness prevention at high temperature.
S30, checking the strength of the supporting thin sheet 4 of the bearing seat 1, and continuously adjusting the structural size and/or shape and/or number of the supporting thin sheet 4 until the stress of the supporting thin sheet 4 is less than or equal to the allowable stress of the bearing seat material so as to complete the design of the high-temperature magnetic transmission pump; wherein the support foil 4 is located at the point where the bearing housing 1 cooperates with the slide bearing 2.
In this embodiment, the rigidity of the sliding bearing 2 is high, and in a normal temperature cold state, the supporting sheet 4 on the bearing housing 1 is pushed up by the sliding bearing 2 to be bent and deformed due to interference, and the interference is large, and the deflection caused by bending is large, so that the sliding bearing has a large stress. The interference magnitude of one side (radius) can be regarded as deflection y generated by the thin sheet 4 supported by the bearing seat 1; according to cantilever beam deflection calculation formula y=fl 3 3EI and the structural dimensions of the sheet 4 (where F is the force at the support point, L is the distance from the support point to the fixed end (see FIGS. 6 and 7), E is the elasticity of the materialModulus, I is the moment of inertia of the cross section of the lamina 4 with respect to the bending direction), the force F to which the lamina 4 structure is designed can be calculated;
from this, the bending moment m=fl, F, see fig. 6, experienced by the sheet 4 beam can be calculated; calculating the stress at the sheet 4 of the bearing seat 1 according to a cantilever beam stress calculation formula sigma=M/W (W is the bending-resistant section modulus of the sheet 4), comparing with the allowable stress of the material of the bearing seat 1, and if the allowable stress is not more than the allowable stress, completing the design; if not, the structural size and shape of the sheet 4 are changed, such as by changing the number of sheets L, h or sheets 4, and the verification is calculated again until the stress meets the requirement.
When the same deformation amount caused by the interference structure is generated, the force required by bending deformation of the cantilever beam type thin sheet 4 (also called as a supporting thin sheet 4 or a thin sheet 4) is far smaller than that of the cylindrical rigid thick-wall cylinder, so that the stress of the sliding bearing 2 and the bearing seat 1 is obviously reduced under the condition of large excessive assembly, the assembly and the disassembly are easy, and the sliding bearing can work normally under the normal temperature and cold state; when working at the design temperature, the temperature rise causes the interference between the bearing seat 1 and the sliding bearing 2 to be reduced, but the bearing seat 1 and the sliding bearing 2 are still in an interference fit state and are tightly matched, so that the bearing seat is not loosened at high temperature, and meanwhile, the coaxiality between the bearing seat and the sliding bearing is maintained, and the problem and the defect of the original high-temperature magnetic pump are thoroughly solved.
Example two
Based on the first embodiment, the high-temperature magnetic drive pump manufactured by the design and development method of the high-temperature magnetic drive pump of the first embodiment. The remaining parts are the same as in the prior art.
For example, the sliding bearing seat 1 of the high-temperature magnetic drive pump is formed by an electric spark wire cutting method on an integrated sheet 4 on the inner surface, and a plurality of gaps 3 with closed ends are cut out uniformly along the circumference to form a plurality of thinner supporting sheets with the same size. The slit 3 formed by wire cutting itself becomes a movable space required for radial bending deformation of the support sheet 4.
Therefore, the high-temperature magnetic drive pump using the technology thoroughly solves the defects of low pump efficiency, poor running reliability and inconvenient maintenance of the sliding bearing 2 of the original leakage-free magnetic drive pump under the high-temperature working condition, is suitable for the requirement of leakage-free conveying medium under the high-temperature and variable-temperature conditions, and has the advantages of low running vibration, high efficiency, high reliability and convenient installation and maintenance.
The detailed description of the present application is not prior art, and thus is not described in detail herein.
It will be understood that the terms "a" and "an" should be interpreted as referring to "at least one" or "one or more," i.e., in one embodiment, the number of elements may be one, while in another embodiment, the number of elements may be plural, and the term "a" should not be interpreted as limiting the number.
Although the terms bearing housing 1, slide bearing 2, slit 3, lamella 4, spiral 5, slit 3 start, slit 3 end etc. are used more herein, the possibility of using other terms is not excluded. These terms are used merely for convenience in describing and explaining the essence of the present application; they are to be interpreted as any additional limitation that is not inconsistent with the spirit of the present application.
The present application is not limited to the above-mentioned preferred embodiments, and any person can obtain other products in various forms under the teaching of the present application, but any changes in shape or structure of the products are within the scope of protection of the present application.
Claims (9)
1. The design and development method of the high-temperature magnetic drive pump is characterized by comprising the following steps of:
s00, uniformly arranging a plurality of spiral gaps with the same shape and length on the inner hole surface of a bearing seat of a magnetic drive pump along the circumferential direction, arranging openings of the spiral gaps on the inner hole surface, and arranging the tail ends of the spiral gaps in a base body of the bearing seat;
the lengths of the initial end and the tail end of the adjacent spiral gaps are positioned at the same circumferential azimuth angle in the circumferential direction, so that the inner surface of the bearing seat forms a sheet-shaped structure, one end of the sheet-shaped structure is suspended, and the other end of the sheet-shaped structure is fixed on a base body of the bearing seat to form an cantilever type sheet serving as a supporting sheet;
wherein the angle of each spiral gap along the circumferential direction is larger than 360 degrees/the number of the spiral gaps;
s10, calculating the expansion difference between the room temperature and the required design temperature of the magnetic drive pump at the matching surface between the bearing seat and the sliding bearing;
s20, determining the size of an inner hole of the bearing seat according to the expansion difference and the outer diameter size of the sliding bearing and the interference requirement at the design temperature;
s30, checking the strength of the supporting thin sheet of the bearing seat, and continuously adjusting the structural size and/or shape and/or number of the supporting thin sheet until the stress of the supporting thin sheet is smaller than or equal to the allowable stress of the bearing seat material so as to complete the design of the high-temperature magnetic transmission pump;
wherein the support sheet is positioned at a position where the bearing housing is matched with the sliding bearing.
2. The method according to claim 1, wherein in step S00, the spiral slit is involute or arc or approximate arc.
3. The design and development method of a high-temperature magnetic drive pump according to claim 1, wherein in the step S00, the ratio of the radial distance between the end of the spiral gap and the surface of the inner hole of the bearing seat to the length of the spiral gap is 0.1-0.25.
4. A design development method for a high-temperature magnetic drive pump according to claim 3, wherein in step S00, a distance is set from a spiral start of said spiral slit so that a thickness of said support sheet has a wall thickness of at least 0.5mm, wherein said spiral start intersects with an inner surface of said bearing housing inner hole.
5. The method according to claim 1, wherein in the step S00, the number of the spiral slits is not less than six.
6. The method according to any one of claims 1 to 5, wherein in step S10, the expansion difference is calculated according to the linear expansion coefficient of the bearing housing, the linear expansion coefficient of the sliding bearing material, the size of the matching portion of the outer diameter of the sliding bearing, and the design temperature required for the magnetic drive pump.
7. The design and development method of a high temperature magnetic drive pump according to any one of claims 1 to 5, wherein in step S20, the size of the inner hole of the bearing seat is determined according to the expansion difference, the outer diameter size of the sliding bearing, and the interference, wherein the interference is to increase the pretightening force based on the expansion difference, so that the expansion difference is increased, and the expansion difference is replaced by the interference, so as to achieve the anti-loose effect at high temperature.
8. The method for designing and developing a high-temperature magnetic drive pump according to claim 7, wherein the interference is 115% -130% of the expansion difference.
9. A high-temperature magnetic drive pump, characterized in that the pump is manufactured by designing and developing the design and development method of the high-temperature magnetic drive pump according to any one of claims 1-8.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202211649199.1A CN116044773B (en) | 2022-12-21 | 2022-12-21 | High-temperature magnetic drive pump and design and development method thereof |
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| CN202211649199.1A CN116044773B (en) | 2022-12-21 | 2022-12-21 | High-temperature magnetic drive pump and design and development method thereof |
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| CN116044773A CN116044773A (en) | 2023-05-02 |
| CN116044773B true CN116044773B (en) | 2023-07-18 |
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| US5660481A (en) * | 1987-05-29 | 1997-08-26 | Ide; Russell D. | Hydrodynamic bearings having beam mounted bearing pads and sealed bearing assemblies including the same |
| ES2087227T3 (en) * | 1990-12-27 | 1996-07-16 | Ebara Corp | AXLE SLEEVE MADE OF CERAMIC. |
| JP2005098315A (en) * | 2003-09-22 | 2005-04-14 | Ntn Corp | Hydrodynamic bearing apparatus |
| CN202579282U (en) * | 2012-04-11 | 2012-12-05 | 丹东克隆先锋泵业有限公司 | Main shaft sliding bearing of magnetic pump |
| CN204164177U (en) * | 2014-10-15 | 2015-02-18 | 哈尔滨东安发动机（集团）有限公司 | A kind of bearing sleeve structure |
| CN109268303B (en) * | 2018-11-12 | 2024-01-05 | 丹东通博泵业有限公司 | Magnetic drive pump sliding bearing assembly and magnetic drive pump |
| CN214330966U (en) * | 2021-01-13 | 2021-10-01 | 江苏海狮泵业制造有限公司 | Novel anti-loose sliding bearing assembly of magnetic pump |
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2022
- 2022-12-21 CN CN202211649199.1A patent/CN116044773B/en active Active
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